JP2009108762A - Rotary fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce vibration by inertial force of a rotation preventive mechanism in high speed rotation, in a rotary fluid machine for enabling a cylinder and an annular piston to relatively make eccentric rotary motion, by arranging the annular piston in an annular space formed in the cylinder. <P>SOLUTION: This rotary fluid machine is provided for eccentrically rotating the piston 40 to the cylinder 35, and is provided with a rear head 50 supporting the piston 40 on the back face side of a piston side end plate 41 of the piston 40, and also has a plurality of pistons 101 arranged on the piston side end plate 41 of the piston 40 and a plurality of guide holes 102 arranged in the rear head 50, inserting the respective pistons 101 and guiding the movement of the pistons, and is provided with the rotation preventive mechanism 100 regulating rotation of the piston 40. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a rotary fluid machine in which an annular piston is disposed in an annular space formed in a cylinder, and the cylinder and the annular piston relatively eccentrically rotate.

  2. Description of the Related Art Conventionally, in a compressor or the like that compresses refrigerant, an annular piston is disposed in an annular space (cylinder chamber) formed in a cylinder, and the cylinder and the annular piston rotate relatively eccentrically. A type fluid machine may be used.

  As an example of such a rotary fluid machine, for example, a rotary fluid machine described in Patent Document 1 is known. This rotary fluid machine is a rotary fluid machine in which an annular piston revolves with respect to a cylinder. In this rotary fluid machine, as shown in FIG. 6 of Patent Document 1, a cylinder chamber is partitioned into a high pressure chamber and a low pressure chamber by a concave blade. This concave blade can slide in the radial direction of the cylinder (referred to as the X direction). Further, a part of the piston is provided with a flat portion on which the concave portion of the blade slides. Thereby, the blade can slide with respect to the piston in a direction perpendicular to the X direction. Therefore, the direction in which the piston can move is the radial direction of the cylinder and the direction orthogonal to the radial direction of the cylinder. That is, the rotation prevention mechanism is constituted by the blade, the piston, and the cylinder, and the rotation of the piston is prevented. FIG. 3 of Patent Document 1 also describes an example in which an Oldham coupling is constituted by a piston, an Oldham ring, and a lower housing to prevent rotation of the piston.

As described above, in the rotary fluid machine in which the annular piston revolves with respect to the cylinder, the rotation prevention mechanism such as an Oldham coupling is provided to prevent the rotation of the annular piston.
Korean Patent No. 10-0436864 Specification

  However, as described above, the rotation preventing mechanism having the Oldham ring has a problem that vibration based on the inertial force increases during high-speed operation because the Oldham ring reciprocates. Moreover, in order to construct such an Oldham joint, it is necessary to form a key and a key groove in the cross direction, so that complicated processing is required, leading to an increase in manufacturing cost, for example.

  Further, as described above, the rotation prevention mechanism including the blade, the piston, and the cylinder requires a certain thickness of the blade to ensure stable sliding and durability. As a result, the mass of the blade increases, and vibration based on the inertial force of the blade may increase.

  The present invention has been made paying attention to the above-described problem, and an object thereof is to reduce vibration due to inertial force of the rotation prevention mechanism during high-speed operation.

  In order to solve the above problems, the present invention includes a plurality of pins (101) and a plurality of guide holes (102) into which the pins (101) are inserted to guide the movement of the pins (101). A rotation prevention mechanism (100) for restricting rotation of the movable side cooperating member (40) is provided.

Specifically, the first invention is:
A cylinder (35) having an annular cylinder chamber (60, 65) and having an end plate (36) on the back surface; and being eccentric to the cylinder (35) and housed in the cylinder chamber (60, 65); The cylinder chamber (60, 65) is divided into an outer working chamber (60) and an inner working chamber (65), and an annular piston (40) having an end plate (41) on the back surface, and each of the working chambers (60, 65). ) Is divided into a high pressure side (61,66) and a low pressure side (62,67), and either one of the piston (40) and the cylinder (35) is a fixed side working member ( 35), the other is a movable side cooperating member (40), and the movable side cooperating member (40) rotates eccentrically with respect to the fixed side cooperating member (35). And
A support member (50) for supporting the movable side cooperating member (40) on the back side of the end plate (41) of the movable side cooperating member (40);
A plurality of pins (101) provided on one of the opposing members of the end plate (41) of the movable side cooperating member (40) and the support member (50), and each of the pins provided on the other opposing member An anti-rotation mechanism (100) that includes a plurality of guide holes (102) into which the pin (101) is inserted and guides the movement of the pin (101) to restrict the rotation of the movable side cooperating member (40); ,
It is characterized by having.

In addition, the second invention,
A cylinder (35) having a cylinder chamber (61, 66, 67) with a C-shaped groove and having an end plate (36) on the back surface, and the cylinder chamber (61, 66) eccentric to the cylinder (35) , 67) and a piston (40) having an end plate (41) on the back, and abutting against one end of the piston (40) in the cylinder chamber (61, 66, 67), the cylinder chamber ( 61, 66, 67) is provided with a blade (45) that divides the outer working chamber (61) and the inner working chamber (67), and either one of the piston (40) and the cylinder (35) is on the fixed side. Rotating fluid configured as a working member (35) and the other as a movable side cooperating member (40) in which the movable side cooperating member (40) rotates eccentrically with respect to the fixed side cooperating member (35) A machine,
A support member (50) for supporting the movable side cooperating member (40) on the back side of the end plate (41) of the movable side cooperating member (40);
A plurality of pins (101) provided on one of the opposing members of the end plate (41) of the movable side cooperating member (40) and the support member (50), and each of the pins provided on the other opposing member An anti-rotation mechanism (100) that includes a plurality of guide holes (102) into which the pin (101) is inserted and guides the movement of the pin (101) to restrict the rotation of the movable side cooperating member (40); ,
It is characterized by having.

  Accordingly, the movement of the pin (101) is regulated by the guide hole (102), so that the rotation of the movable side cooperating member (40) is reliably prevented, and the piston (40) is fixed to the fixed side cooperating member ( 35). And, the rotation prevention mechanism (100) by the pin (101) and the guide hole (102) is not the reciprocation of the member, but the rotation movement of the pin (101) is performed like the rotation prevention mechanism by the Oldham coupling. The rotation prevention mechanism itself does not become a vibration source. In particular, the vibration is low even during high speed operation.

In addition, the third invention,
In any of the first and second inventions,
A seal ring (70) for forming a back pressure space for pressing the movable side cooperating member (40) against the fixed side cooperating member (35) is provided between the opposing members.
A seal ring groove (103) for fitting the seal ring (70) is formed in the opposing member on the guide hole (102) side.

  With this configuration, interference between the guide hole (102) and the seal ring groove (103) does not occur during operation. Therefore, the rotary fluid machine can be designed without considering interference between the guide hole (102) and the seal ring (70) during operation. In other words, the design is easier than in the case where the guide hole (102) and the seal ring (70) are provided in separate members. Further, in the case where the guide hole (102) and the seal ring groove (103) are provided in separate members, the piston (40) is used to avoid interference between the guide hole (102) and the seal ring groove (103) during operation. ) And the end plate of the cylinder (35) need to be enlarged. However, according to the present invention, these end plates can be designed to be small.

In addition, the fourth invention is
In any of the first and second inventions,
In the guide hole (102), a sleeve harder than the opposing member on the guide hole (102) side is fitted.

  For example, if the guide hole (102) partially slides repeatedly with the pin (101), there is a possibility of uneven wear. However, with such a configuration, the wear resistance can be improved.

In addition, the fifth invention,
In the first invention,
The blade (45) is formed in a plate shape, and the blade (45) is configured such that the longitudinal direction of the blade (45) can freely move in the X-axis direction that is the radial direction of the cylinder (35) with respect to the cylinder (35). The thickness direction of (45) is configured to be movable in the Y direction perpendicular to the X-axis direction with respect to the piston (40).

  In the rotary fluid machine including the blade (45) configured as in the present invention, the blade, piston, and cylinder can be used as an anti-rotation mechanism. In this case, stable sliding and durability are possible. In order to guarantee the performance, it is necessary to secure a certain thickness (width in the Y direction) of the blade (45). However, in the present invention, the rotation of the piston (40) is prevented by the rotation prevention mechanism (100) including the pin (101) and the guide hole (102). Therefore, stable sliding and durability can be ensured even if the thickness of the blade (45) is reduced compared to a rotary fluid machine that uses an Oldham coupling consisting of a blade, piston, and cylinder as an anti-rotation mechanism. It becomes possible. In other words, in the present invention, the vibration due to the reciprocating motion (blade inertia force) of the blade (45) is reduced during high-speed operation due to the downsizing of the blade (45).

In addition, the sixth invention,
In any of the first and second inventions,
The cylinder (35) is configured as a fixed side cooperative member (35), and the piston (40) is configured as a movable side cooperative member (40).

  Thereby, in the rotary fluid machine in which the cylinder (35) is fixed and the piston (40) is movable, the rotation of the piston (40) is prevented. Then, the piston (40) revolves with respect to the cylinder (35).

In addition, the seventh invention,
In any of the first and second inventions,
The piston (40) is configured as a fixed side cooperating member (35), and the cylinder (35) is configured as a movable side cooperating member (40).

  Thereby, in the rotary fluid machine in which the piston (40) is fixed and the cylinder (35) is movable, the rotation of the cylinder (35) is prevented. Then, the cylinder (35) revolves with respect to the piston (40).

  According to the first and second inventions, rotation of the movable side cooperating member (40) is prevented by the pin (101) and the guide hole (102). The anti-rotation mechanism (100) by the pin (101) and the guide hole (102) does not reciprocate like the anti-rotation mechanism by the Oldham coupling, so the anti-rotation mechanism itself does not become a vibration source. It is possible to reduce vibration during high-speed operation. Further, the Oldham joint needs to be provided with a protruding key and a recessed key groove on the back surface of the ring member, and the simultaneous processing of the front and back surfaces is not easy, so the processing is complicated. On the other hand, the rotation prevention mechanism (100) using the pin (101) and the guide hole (102) only needs to set the diameter of the pin (101) and the guide hole (102). Is unnecessary, and the cost can be reduced.

  According to the third aspect of the invention, interference between the guide hole (102) and the seal ring groove (103) does not occur during operation. That is, the guide hole (102) and the seal ring groove (103) can be designed more easily than those provided in separate members. Further, the end plates of the fixed side cooperative member (35) and the movable side cooperative member (40) can be designed to be small.

  Further, according to the fourth invention, the wear resistance of the member provided with the guide hole (102) can be improved.

  According to the fifth invention, the thickness of the blade (45) can be made smaller than that of a rotary fluid machine in which an Oldham coupling composed of a blade, a piston, and a cylinder is used as an anti-rotation mechanism. That is, according to the present invention, vibration caused by the reciprocating motion (blade inertia force) of the blade (45) can be reduced during high-speed operation.

  According to the sixth aspect, in the rotary fluid machine in which the cylinder (35) is fixed and the piston (40) is movable, the rotation of the piston (40) is prevented.

  According to the seventh invention, in the rotary fluid machine in which the piston (40) is fixed and the cylinder (35) is movable, the rotation of the cylinder (35) is prevented.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The following embodiments are essentially preferable examples, and are not intended to limit the scope of the present invention, its application, or its use. In the following description of each embodiment and modification, components having the same functions as those described once will be given the same reference numerals and description thereof will be omitted.

Embodiment 1 of the Invention
As an embodiment of the present invention, for example, a compressor used for compressing refrigerant sucked from an evaporator and discharging it to a condenser in a refrigerant circuit of an air conditioner will be described.

-Overall configuration of compressor (1)-
As shown in FIG. 1, the compressor (1) includes a motor (20) (drive mechanism) and a compression mechanism (30) housed in a casing (10), and is configured as a completely sealed type.

  The casing (10) has a pair of cylindrical portions (12) formed in a vertically long cylindrical shape and a pair of flanges formed so as to protrude outward at both ends of the cylindrical portion (12). This is a vertically long sealed container constituted by the end plate portion (13). The one end plate portion (13) that closes the upper end side of the cylindrical portion (12) is provided with a discharge pipe (14) that penetrates the end plate portion (13) in the thickness direction, and the cylindrical portion ( 12) is provided with a suction pipe (15) penetrating the cylindrical portion (12) in the thickness direction.

  Here, as shown in FIG. 1, the discharge pipe (14) communicates with the inside of the casing (10). On the other hand, the suction pipe (15) is connected to a compression mechanism (30) in the casing (10). That is, in the compressor (1), the refrigerant compressed by the compression mechanism (30) is discharged into the internal space of the casing (10), and then passes through the discharge pipe (14) to the outside of the casing (10). It is a so-called high pressure dome type compressor that is configured to be delivered and in which the inside of the casing (10) is in a high pressure state. That is, the space in the casing (10) becomes the high-pressure space (S2).

  Inside the casing (10), an electric motor (20) as a drive mechanism and a compression mechanism (30) are arranged in order from top to bottom. Further, a drive shaft (25) is disposed inside the casing (10) so as to extend in the cylindrical axis direction within the cylindrical portion (12) of the casing (10). The drive shaft (25) The compression mechanism (30) and the electric motor (20) are drivingly connected via the. In addition, the bottom part in the said casing (10) of airtight container becomes the storage part (59) in which the lubricating oil supplied to each sliding part etc. of the said compression mechanism (30) is stored.

  The drive shaft (25) has a main shaft portion (26) and an eccentric portion (27). The eccentric portion (27) is formed in a columnar shape having a larger diameter than the main shaft portion (26) at a position near the lower end of the drive shaft (25). The eccentric portion (27) is provided such that the shaft center is eccentric with respect to the shaft center of the main shaft portion (26). Further, the eccentric part (27) is fixed to the piston (40) so as to be integrally rotatable in a state of passing through a piston (40) of the compression mechanism (30) described later.

  Further, a through hole (25a) as an oil supply passage extending upward from the lower end of the drive shaft (25) is formed in the drive shaft (25). As a result, the lubricating oil in the reservoir (59) located at the bottom in the casing (10) rises in the through hole (25a) due to the high pressure in the casing (10), and the compression mechanism (30 ) To each sliding part.

  The electric motor (20) includes a stator (21) and a rotor (22). The stator (21) is fixed to the inner surface of the cylindrical portion (12) of the casing (10). The main shaft portion (26) of the drive shaft (25) passes through the rotor (22), and is arranged inside the substantially cylindrical stator (21) in this state.

  The compression mechanism (30) includes a cylinder (35) as a fixed side cooperating member, a rear head (50), and a piston (40) as a movable side cooperating member (40). The cylinder (35) is formed in a bottomed cylindrical shape, and is disposed on the upper side of the rear head (50) so that the bottom is positioned upward. Thereby, the space for accommodating the said piston (40) is formed between both.

  The piston (40) has a cylindrical bearing portion (42) fitted to the eccentric portion (27) of the drive shaft (25), and the outer peripheral side of the bearing portion (42) with respect to the bearing portion (42). The annular piston body (43), concentrically positioned, and the bearing (42) and the annular piston body (43) are integrated at the lower end (one axial end of the compression mechanism (30)). And a disc-shaped piston side end plate (41). The said annular piston main-body part (43) is formed in the substantially C-shaped shape by which a part of annular ring was parted, and this parted part comprises the blade groove | channel mentioned later.

  The rear head (50) is a member (support member) that supports the piston (40). The rear head (50) is a thick disk-shaped member that is fixed to the inner peripheral surface of the casing (10) at the outer peripheral edge thereof, and the outer peripheral portion is in close contact with the cylinder (35). To be fixed. In addition, the main shaft portion (26) of the drive shaft (25) passes through the central portion of the rear head (50), and the main shaft portion (26) can be rotated on the inner peripheral surface of the through hole. A supporting sliding bearing (50a) is provided. The rear head (50) is provided with a seal ring groove (103) for accommodating the seal ring (70), as will be described in detail later.

  The cylinder (35) includes a cylinder-side end plate (36), an outer cylinder part (38) (also referred to as a peripheral part), and a bearing part (37). The outer cylinder part (38) has a rear head (50). On the other hand, the drive shaft (25) is rotatably supported by the bearing portion (37).

  Specifically, the cylinder side end plate (36) is formed in a thick disk shape, and the outer cylinder part (38) located on the outer peripheral side of the cylinder side end plate (36) is welded or the like. Thus, the rear head (50) fixed to the inner surface of the cylindrical portion (12) of the casing (10) is fixed with a bolt or the like. A cylindrical bearing portion (37) that bulges upward is formed at the center of the cylinder side end plate (36), and the bearing portion (37) includes the bearing portion (37). ) In the vertical direction, a slide bearing (37a) is provided for rotatably supporting the main shaft portion (26) of the drive shaft (25).

  The outer cylinder part (38) is formed in a substantially cylindrical shape so as to bulge downward from the lower surface of the cylinder side end plate (36), and penetrates the outer cylinder part (38) in the radial direction. A suction port (39) is formed. The suction port (39) has one end opened to a space formed by the cylinder (35) and the rear head (50), and the other end connected to the suction pipe (15). A part of a suction passage for sucking the refrigerant into the space is configured. That is, the suction port (39) forms part of the low pressure space (S1).

  Further, a substantially cylindrical inner cylinder part (52) arranged concentrically with the outer cylinder part (38) is projected on the lower surface of the cylinder side end plate (36), whereby the inner cylinder part (52) A cylinder chamber (60, 65) as a compression chamber is formed between the cylinder portion (52) and the outer cylinder portion (38). The annular piston body (43) of the piston (40) is positioned in the annular cylinder chamber (60, 65) as shown in FIG.

  More specifically, the outer peripheral surface of the outer cylinder part (38) and the outer peripheral surface of the inner cylinder part (52) are cylindrical surfaces arranged on the same center, and the cylinder chamber (60, 65) is interposed between them. ) Is formed. The annular piston body (43) of the piston (40) has an outer peripheral surface having a smaller diameter than the inner peripheral surface of the outer cylinder portion (38), and an inner peripheral surface having a larger diameter than the outer peripheral surface of the inner cylinder portion (52). Is formed. As a result, an outer cylinder chamber (60) is formed between the outer peripheral surface of the annular piston main body (43) and the inner peripheral surface of the outer cylinder (38). An inner cylinder chamber (65) is formed between the peripheral surface and the outer peripheral surface of the inner cylinder part (52).

  That is, the cylinder side end plate (36), the piston side end plate (41), the outer cylinder portion (38), and the annular piston main body portion (43) form an outer cylinder chamber (60), and the cylinder side end plate (36) The piston-side end plate (41), the inner cylinder part (52), and the annular piston body part (43) form an inner cylinder chamber (65). Also, between the cylinder side end plate (36), piston side end plate (41), bearing portion (42) of the piston (40) and inner cylinder portion (52), the inner peripheral side of the inner cylinder portion (52) Thus, an operation space (68) for allowing the eccentric rotation operation of the bearing portion (42) is formed. 1 and 2, the operation space (68) is configured to be a high-pressure space.

  The piston (40) and the cylinder (35) are in a state in which the outer peripheral surface of the annular piston body (43) and the inner peripheral surface of the outer cylinder (38) are substantially in contact at one point (strictly speaking, In a micron-order gap where refrigerant leakage does not become a problem), the inner peripheral surface of the annular piston body (43) and the inner cylinder ( 52) is substantially in contact with the outer peripheral surface at one point.

  In addition, plane portions (38a, 52a) that are substantially parallel to each other are formed at opposing positions on the inner peripheral surface of the outer cylinder portion (38) and the outer peripheral surface of the inner cylinder portion (52). These flat portions (38a, 52a) are provided so as to be orthogonal to the radial direction of the cylinder (35). As will be described later, the cylinder chamber (60, 65) is replaced with the high pressure chamber (61, 66). And a substantially rectangular parallelepiped blade (45) which divides into a low pressure chamber (62, 67) and is in sliding contact with both end faces in the extending direction.

  As described above, the cylinder (35) is provided with a suction port (39) communicating with the suction pipe (15). One end of the suction port (39) is connected to the outer cylinder chamber (60). Open to the low pressure chamber (62). The annular piston body (43) has a through hole (53) that communicates the low pressure chamber (62) of the outer cylinder chamber (60) and the low pressure chamber (67) of the inner cylinder chamber (65). Has been.

  On the other hand, the cylinder (35) is formed with an outer discharge port (54) and an inner discharge port (55). These discharge ports (54, 55) respectively penetrate the cylinder side end plate (36) of the cylinder (35) in the thickness direction. The lower end of the outer discharge port (54) opens to face the high pressure chamber (61) of the outer cylinder chamber (60), and the lower end of the inner discharge port (55) is the high pressure chamber (66) of the inner cylinder chamber (65). ). The discharge ports (54, 55) are provided with discharge valves (not shown) for opening and closing the discharge ports (54, 55).

  The annular piston main body (43) and the front end surface (the upper end surface in FIG. 1) of the bearing (42) of the piston (40) are both in sliding contact with the cylinder end plate (36) of the cylinder (35). The front end surface (lower end surface in FIG. 1) of the inner cylinder portion (52) of the cylinder (35) is also in sliding contact with the piston side end plate (41) of the piston (40). Thus, the cylinder chamber (60, 65) formed by the inner cylinder part (52) of the cylinder (35) and the piston (40) is in an airtight state. In addition, although mentioned later in detail, in order to maintain this airtight state, it is comprised so that pressing force may act on the said piston (40) from the back side.

  As shown in FIGS. 1 and 3, a seal ring groove (103) is provided on the upper surface of the rear head (50) corresponding to the piston side end plate (41) of the piston (40). 103) contains a seal ring (70). Thereby, the seal ring (70) divides the space between the rear head (50) and the piston (40) in the radial direction.

  The space on the inner peripheral side of the seal ring (70) communicates with the high-pressure space (S2) in the casing (10), and passes through the through hole (25a of the drive shaft (25) from the storage part (59). ) The high-pressure lubricating oil that has passed through the inside is supplied. That is, since the space inside the seal ring (70) is in a high pressure state, a back pressure that presses the piston (40) toward the cylinder (35) acts.

  Here, a separation force that separates from the cylinder (35) is generated in the piston (40) by the internal pressure of the cylinder chamber (60, 65). On the other hand, by applying the pressing force as described above to the piston (40), the piston (40) can be prevented from separating from the cylinder (35), and the piston (40) The cylinder chamber (60, 65) formed by the cylinder and the cylinder (35) is kept airtight.

  On the other hand, the space on the outer peripheral side of the seal ring (70) is a back pressure space (S3). The pressure in the back pressure space (S3) is caused by the lubricating oil that enters beyond the seal ring (70) or the lubricating oil that leaks from the bearing through the cylinder chamber (60, 65). The intermediate pressure is higher than that of 39) and lower than that of the high-pressure space (S2) in the casing (10). Thus, the pressure in the back pressure space (S3) also acts to press the piston (40) from the back side.

  Further, in this compressor (1), a plurality of pins (101) and a plurality of guide holes (102) into which the pins (101) are inserted to guide the movement of the pins (101), piston (40) ) Rotation prevention mechanism (100).

  Specifically, in the present embodiment, the plurality of pins (101) are provided on the surface of the piston side end plate (41) on the side facing the rear head (50). FIG. 3 shows an example in which three pins (101) are provided. In addition, the diameter of each pin (101) shall be d.

  The plurality of guide holes (102) are provided in the rear head (50) as shown in FIG. The diameter D of each guide hole (102) is set to D = d + 2e + δ. Where e is the amount of crank eccentricity (that is, the amount of eccentricity of the eccentric portion (27) relative to the main shaft portion (26)), and δ is a minute gap set between the pin (101) and the guide hole (102). It is. Accordingly, the movement of the piston (40) in the rotation direction is limited by the pins (101) and the guide holes (102) corresponding to the pins (101).

-Blade-
As described above, the compression mechanism (30) includes the blade (45) that partitions the cylinder chamber (60, 65) into a high pressure chamber (61, 66) and a low pressure chamber (62, 67), respectively. Yes. The blade (45) is located on the radial line of the cylinder chamber (60, 65) from the inner peripheral wall surface (the outer peripheral surface of the inner cylinder portion (52)) of the cylinder chamber (60, 65) to the outer peripheral side. It is a substantially rectangular parallelepiped shaped member configured to extend through the wall portion (the inner peripheral surface of the outer cylinder portion (38)) through the dividing portion of the annular piston main body portion (43). In the blade (45), both end faces in the extending direction (both end faces on the outer cylinder part (38) side and inner cylinder part (52) side) and both side faces in contact with the annular piston body part (43) are parallel to each other. It is a flat surface.

  That is, the blade (45) is inserted between the blade groove side surfaces (58, 58) of the annular piston main body (43), and both end surfaces of the blade (45) in the extending direction are the outer cylinder portion (38) and The flat surface portions (38a, 52a) of the inner cylinder portion (52) are substantially in surface contact, and both side surfaces of the blade (45) are substantially in contact with the blade groove side surfaces (58, 58) of the annular piston body portion (43). It is arrange | positioned so that surface contact may be carried out.

  Thereby, the blade (45) has the flat surfaces at both ends in the extending direction in sliding contact with the flat surface portions (38a, 52a) of the outer cylinder portion (38) and the inner cylinder portion (52), and the flat surfaces on both side surfaces are the annular shape. The piston body portion (43) is slidably brought into contact with the plane portion (38a, 52a) and the annular piston body portion (43).

  In the above configuration, when the piston (40) coupled to the drive shaft (25) rotates in an eccentric state with respect to the cylinder (35), the rotation of the piston (40) causes the pin (101) and the guide hole to rotate. This is prevented by the rotation prevention mechanism (100) comprising (102). As a result, as shown in FIG. 4, the annular piston main body (43) of the piston (40) slides in the extending direction of the blade (45), and the outer cylinder (38) together with the blade (45). ) And the flat surface portions (38a, 52a) of the inner cylinder portion (52), and revolves with respect to the cylinder (35). The operation of the annular piston main body (43) will be described in detail later. By sliding the blade (45) with respect to the annular piston main body (43) and the flat surface (38a, 52a), the annular piston main body (43). And the cylinder (35) are moved in order from (A) to (D) in FIG. 4, and the refrigerant is compressed in the cylinder chamber (60, 65). FIG. 4 is a view showing the operating state of the compression mechanism (30) according to this embodiment, and the annular piston main body (43) is shown at intervals of 90 ° from (A) to (D) of FIG. It shows a state of moving in the clockwise direction.

  As described above, in the compressor (1), the rotation of the piston (40) is reliably prevented by the pin (101) and the guide hole (102). Therefore, the annular piston main body (43) has a movement in the extending direction of the blade (45), that is, in the radial direction, and a direction in which the flat portion (38a, 52a) extends, that is, in a direction perpendicular to the radial direction. Makes a synthesized movement.

-Driving action-
Next, the operation of the compressor (1) will be described.

  First, when the electric motor (20) is started, the rotation of the rotor (22) is transmitted to the piston (40) of the compression mechanism (30) via the drive shaft (25). Then, the annular piston main body (43) of the piston (40) reciprocates (advances and retreats) along the blade (45), and the annular piston main body (43) and the blade (45) are integrated. And slides in a direction perpendicular to the reciprocating direction with respect to the outer cylinder portion (38) and the inner cylinder portion (52) of the cylinder (35). Further, since the pin (101) is inserted into the guide hole (102) and rotates along the guide hole (102), the annular piston main body (43) is connected to the outer cylinder portion (38) of the cylinder (35). ) And the inner cylinder part (52) revolve without rotating, and the compression mechanism (30) performs a predetermined compression operation.

  Specifically, in the outer cylinder chamber (60) of the compression mechanism (30), the volume of the low-pressure chamber (62) is almost minimum in the state of FIG. When the volume of the low-pressure chamber (62) increases as it rotates clockwise in the figure and changes to the states of (B) to (D) in FIG. 4, the refrigerant flows into the suction pipe (15) and The air is sucked into the low pressure chamber (62) through the suction port (39).

  When the drive shaft (25) makes one revolution and again enters the state of FIG. 4 (A), the suction of the refrigerant into the low pressure chamber (62) is completed. The low-pressure chamber (62) is now a high-pressure chamber (61) in which the refrigerant is compressed, and a new low-pressure chamber (62) is formed across the blade (45). When the drive shaft (25) further rotates, the suction of the refrigerant is repeated in the low pressure chamber (62), while the volume of the high pressure chamber (61) decreases, and the refrigerant is compressed in the high pressure chamber (61). When the pressure in the high-pressure chamber (61) reaches a set value when the pressure in the high-pressure chamber (61) reaches a set value, the valve is opened by the high-pressure refrigerant in the high-pressure chamber (61), and the high-pressure refrigerant passes from the discharge space to the casing (10). Flows into the high-pressure space (S2).

  On the other hand, in the inner cylinder chamber (65), the volume of the low pressure chamber (67) is almost the minimum in the state of FIG. 4C, and from here the drive shaft (25) rotates clockwise in FIG. When the volume of the low pressure chamber (67) increases as the state changes to the state (D) to (B) of the refrigerant, the refrigerant flows into the suction pipe (15), the suction port (39), and the through hole ( 53) and sucked into the low pressure chamber (67) of the inner cylinder chamber (65).

  When the drive shaft (25) makes one revolution and enters the state of FIG. 4C again, the suction of the refrigerant into the low pressure chamber (67) is completed. The low-pressure chamber (67) is now a high-pressure chamber (66) in which the refrigerant is compressed, and a new low-pressure chamber (67) is formed across the blade (45). When the drive shaft (25) further rotates, the suction of the refrigerant is repeated in the low pressure chamber (67), while the volume of the high pressure chamber (66) is reduced, and the refrigerant is compressed in the high pressure chamber (66). When the pressure in the high pressure chamber (66) reaches a set value when the pressure in the high pressure chamber (66) reaches a set value, the valve is opened by the high pressure refrigerant in the high pressure chamber (66), and the high pressure refrigerant flows from the discharge space to the casing (10). Flows into the high-pressure space (S2).

  In the outer cylinder chamber (60), the refrigerant starts to be discharged approximately at the timing shown in FIG. 4C, and in the inner cylinder chamber (65), the discharge starts approximately at the timing shown in FIG. That is, the discharge timing differs by approximately 180 ° between the outer cylinder chamber (60) and the inner cylinder chamber (65). The high-pressure refrigerant compressed in the outer cylinder chamber (60) and the inner cylinder chamber (65) and flowing into the high-pressure space (S2) in the casing (10) is discharged from the discharge pipe (14) and is condensed in the refrigerant circuit. After passing through the expansion stroke and the evaporation stroke, it is sucked into the compressor (1) again.

  Here, in the space between the piston (40) and the rear head (50), the inner space defined by the seal ring (70) communicates with the high-pressure space (S2), so that it is in a high-pressure state. The piston (40) is pressed from the back side to the cylinder (35) side.

  On the other hand, the lubricating oil in the storage section (59) is pushed upward in the through hole (25a) of the drive shaft (25) by the centrifugal pump action at the lower end of the drive shaft (25), and the compression mechanism (30) The slide bearings (37a, 50a) and the space between the piston (40) and the rear head (50) are provided in the space on the inner peripheral side of the seal ring (70).

-Effect of the embodiment-
As described above, according to the present embodiment, the rotation of the piston (40) is prevented by guiding the movement of the pin (101) through the guide hole (102).

  And the anti-rotation mechanism (100) by the pin (101) and the guide hole (102) does not reciprocate like the anti-rotation mechanism by the Oldham coupling, so the anti-rotation mechanism itself does not become a vibration source. It is possible to reduce vibration during high-speed operation.

  Further, the Oldham joint needs to be provided with a protruding key and a recessed key groove on the back surface of the ring member. However, since the simultaneous processing of the front and back surfaces is not easy, the processing is complicated. On the other hand, the rotation prevention mechanism (100) of this embodiment does not require such complicated processing, and can be expected to reduce costs.

  Further, when the guide hole (102) and the seal ring groove (103) are provided in the same member, the guide hole (102) and the seal ring groove (103) do not interfere with each other during operation. Therefore, the compression mechanism (30) can be designed without considering interference between the guide hole (102) and the seal ring (70) during operation. That is, the design is easier than in the case where the guide hole (102) and the seal ring groove (103) are provided in different members.

  Further, in the case where the guide hole (102) and the seal ring groove (103) are provided in separate members, the piston (40) is used to avoid interference between the guide hole (102) and the seal ring groove (103) during operation. ) And the end plate of the cylinder (35) need to be enlarged. However, according to the present embodiment, these end plates can be designed to be small.

  By the way, in the blade (45) having the above structure, the rotation of the piston (40) can be expected if the blade (45) and the flat portion (38a, 52a) function as an Oldham joint. However, in this case, in order to ensure stable sliding and durability, it is necessary to secure a certain width or more of the blade (45) in the direction orthogonal to the radial direction of the annular piston main body (43). In this case, the mass of the blade (45) increases, and as a result, vibration due to the inertial force of the blade (45) may become a problem.

  On the other hand, in this embodiment, the pin (101) and the guide hole (102) prevent the rotation of the piston (40), so that the torque due to the rotation of the piston (40) acts on the blade (45). do not do. Therefore, in this embodiment, it is possible to ensure stable sliding and durability even with a small blade (45) as compared to a blade, piston, and cylinder that have an anti-rotation mechanism. In other words, in the present embodiment, the size reduction of the blade (45) makes it possible to reduce the vibration caused by the reciprocating motion (blade inertia force) of the blade (45) during high-speed operation.

  Moreover, since the pressure of the refrigerant in the high pressure chamber (61, 66) acting on the flat portion (38a, 52a) does not face the central direction of the annular piston main body (43), the piston (40) is driven by the drive shaft (25). Rotating torque that rotates around. On the other hand, in this embodiment, since it is not necessary to make large the plane part (38a, 52a) of a cylinder (35), the autorotation torque which acts on a piston (40) does not become large. Therefore, the load acting on the pin (101) is small, and the sliding loss due to the pin (101) is also small. Furthermore, since it is not necessary to increase the thickness of the annular piston main body (43), the piston (40) can be downsized.

  The rotation prevention mechanism (100) of the present embodiment can also be adopted in a so-called scroll compressor, but a rotary type in which the cylinder (35) and the piston (40) relatively rotate eccentrically. Manufacture is easier when employed in a fluid machine (referred to as a revolving rotary fluid machine). For example, in a scroll compressor, if the rotation restriction angle is large, the spiral gap is enlarged or reduced. Therefore, in the scroll compressor, it is considered that δ which is a gap between the pin (101) and the guide hole (102) needs to be very small and the number of the pins (101) needs to be increased. On the other hand, the revolution type rotary fluid machine is easy to manufacture because there is no gap increase / decrease due to torsion of the movable side cooperating member (40). Specifically, in the revolution type rotary fluid machine, when the guide hole (102) is provided in the rear head (50), the positional accuracy of the pin (101) and the guide hole (102) is determined between the movable scroll back surface and the housing in the scroll compressor. When the pin (101) and the guide hole (102) are provided, the positional accuracy between the pin (101) and the guide hole (102) can be relaxed. Also, the number of pins (101) can be smaller than that of the scroll compressor.

<< Embodiment 2 of the Invention >>
The compressor (rotary fluid machine) according to the second embodiment of the present invention is different from the first embodiment in the configuration of the cylinder (35), the piston (40), and the blade (45).

  As shown in FIGS. 5 and 6, the piston (40) of the present embodiment includes a cylindrical bearing portion (42) fitted to the eccentric portion (27) of the drive shaft (25), and a bearing portion (42). A space is formed on the outer peripheral side of the annular piston body (43) concentrically with the bearing part (42), and the bearing part (42) and the annular piston body part (43) are integrated at the lower end side. And a disk-shaped piston side end plate (41) provided so as to be formed.

  A linear portion (201) extending linearly in a direction perpendicular to the radial direction is formed in a portion of the annular piston body (43) in the circumferential direction of the annular ring, and a blade described later is formed on the linear portion (201). (45) is slidably fitted.

  Also in this embodiment, the rotation of the piston (40) by the plurality of pins (101) and the plurality of guide holes (102) into which the pins (101) are inserted to guide the movement of the pins (101). A prevention mechanism (100) is configured. Although not shown in FIG. 6, the plurality of pins (101) are provided on the surface of the piston side end plate (41) on the side facing the rear head (50).

  As shown in FIGS. 5 and 7, the cylinder (35) includes an outer cylinder part (38) and an inner cylinder part (52) that are both annular and concentrically arranged. The inner peripheral surface of the outer cylinder portion (38) and the outer peripheral surface of the inner cylinder portion (52) are cylindrical surfaces arranged concentrically with each other, and an annular outer cylinder chamber (60, 65) is formed therebetween. ing. In addition, the part corresponding to the linear part (201) of the said annular piston main-body part (43) in the internal peripheral surface of an outer side cylinder part (38) is formed in the linear form extended in the direction orthogonal to a radial direction.

  The cylinder (35) further includes a cylinder-side end plate (36) formed in a thick disk shape, and the outer cylinder portion (38) faces downward on the outer peripheral side of the cylinder-side end plate (36). The outer cylinder portion (38) is fixed to the rear head (50) fixed to the inner surface of the cylindrical portion (12) of the casing (10) by welding or the like. Further, the inner cylinder part (52) protrudes from the lower surface of the cylinder side end plate (36) on the inner side of the outer cylinder part (38), so that the inner cylinder part (52) and the outer cylinder part ( 38), the outer cylinder chamber (60, 65) as a compression chamber is formed.

  And as shown in FIG. 5, the annular piston main-body part (43) of the said piston (40) is positioned in the said outer cylinder chamber (60,65). The annular piston body (43) has an outer peripheral surface having a smaller diameter than the inner peripheral surface of the outer cylinder portion (38) and an inner peripheral surface having a larger diameter than the outer peripheral surface of the inner cylinder portion (52). As a result, an outer cylinder chamber (60) is formed between the outer peripheral surface of the annular piston main body (43) and the inner peripheral surface of the outer cylinder (38). An inner cylinder chamber (65) is formed between the peripheral surface and the outer peripheral surface of the inner cylinder part (52).

  Specifically, an outer cylinder chamber (60) is formed by the cylinder side end plate (36), the piston side end plate (41), the outer cylinder portion (38), and the annular piston main body portion (43). 36), the piston side end plate (41), the inner cylinder part (52), and the annular piston main body part (43) form an inner cylinder chamber (65).

  Between the cylinder side end plate (36) and inner cylinder part (52) of the cylinder (35) and between the piston side end plate (41) and bearing part (42) of the piston (40), the inner cylinder part (52) An operation space (68) for allowing the eccentric rotation operation of the bearing portion (42) is formed on the inner peripheral side of the shaft (see FIG. 1). In the configuration of FIG. 5, the operation space (68) is configured to be a high-pressure space.

  The piston (40) and the cylinder (35) are in a state in which the outer peripheral surface of the annular piston body (43) and the inner peripheral surface of the outer cylinder (38) are substantially in contact at one point (strictly speaking, In a micron-order gap where refrigerant leakage does not become a problem), the inner peripheral surface of the annular piston body (43) and the inner cylinder ( 52) is substantially in contact with the outer peripheral surface at one point.

  A cylindrical bearing portion (37) that bulges upward is formed at the center of the cylinder side end plate (36) of the cylinder (35), and the bearing portion (37) includes the bearing. A sliding bearing (37a) is provided that rotatably supports the main shaft portion (26) of the drive shaft (25) in a state of passing through the portion (37) in the vertical direction.

  Further, a suction port (39) penetrating the outer cylinder portion (38) in the radial direction is formed in the outer cylinder portion (38). The suction port (39) has one end opened to the low pressure chamber of the outer cylinder chamber (60), and the other end connected to the suction pipe (15). The annular piston body (43) has a through hole (53) that communicates the low pressure chamber (62) of the outer cylinder chamber (60) and the low pressure chamber (67) of the inner cylinder chamber (65). ing.

  On the other hand, the cylinder (35) is formed with an outer discharge port (54) and an inner discharge port (55). These discharge ports (54, 55) are formed so as to penetrate in the thickness direction of the cylinder side end plate (36) of the cylinder (35). The lower end of the outer discharge port (54) opens to face the high pressure chamber (61) of the outer cylinder chamber (60), and the lower end of the inner discharge port (55) opens to the high pressure chamber (66) of the inner cylinder chamber (65). Open to face. These discharge ports (54, 55) are provided with discharge valves (not shown) including check valves for opening and closing the discharge ports (54, 55).

  In the cylinder (35), a blade groove (202) for slidably fitting a substantially rectangular parallelepiped blade (45) is formed at a position corresponding to the linear portion (201) of the piston (40). Arranged along the direction. Specifically, the blade groove (202) includes a first blade groove (202a) formed in the inner cylinder portion (52) and a second blade groove (202b) formed in the cylinder side end plate (36). And the third blade groove (202c) formed in the outer cylinder part (38), and these first to third blade grooves (202a, 202b, 202c) are arranged along the radial direction of the cylinder (35). Are formed continuously in a straight line.

  The vicinity of the portion of the inner cylinder portion (52) where the first blade groove (202a) is formed is formed in a straight line extending in a direction perpendicular to the radial direction, and the first blade groove (202a) The cylinder portion (52) is provided so as to penetrate the central portion in the circumferential direction of the linear portion in the thickness direction. On the other hand, the third blade groove (202c) is provided from the center side end face of the outer cylinder part (38) to the middle part on the outer peripheral side. The blade (45) is fitted into the blade groove (202), and the cylinder chamber (60, 65) is partitioned into a high pressure chamber (61, 66) and a low pressure chamber (62, 67) as will be described later. It is like that.

  Further, the distal end surface of the outer cylinder portion (38) and the distal end surface of the inner cylinder portion (52) are in sliding contact with the upper end surface of the piston side end plate (41), respectively.

  On the other hand, the front end surface (upper end surface in FIG. 1) of the annular piston main body (43) in the piston (40) is a cylinder between the inner cylinder (52) and the outer cylinder (38) of the cylinder (35). The end face of the bearing part (42) of the piston (40) is in sliding contact with the cylinder end panel (36) inside the cylinder part (52) of the cylinder (35). .

  Thereby, an airtight cylinder chamber (60, 65) is formed by the cylinder part (52, 38) and the piston (40) of the cylinder (35).

  In the present embodiment as well, as in the compressor (1) of the first embodiment, in order to maintain the airtight pair of the cylinder chambers (60, 65), the inner peripheral side of the seal ring (70). This space communicates with the high-pressure space (S2) in the casing (10), and is supplied with high-pressure lubricating oil that has passed through the through hole (25a) of the drive shaft (25) from the reservoir (59). It is configured to be. That is, since the space inside the seal ring (70) is in a high pressure state, a back pressure that presses the piston (40) toward the cylinder (35) acts.

  As shown in FIG. 8, the blade (45) is made of a rectangular plate member, and a concave portion (45c) that slides on the linear portion (201) of the piston (40) is formed in the central portion in the longitudinal direction. Has been. The outer side of the recess (45c) is formed in the outer blade part (45a) defining the outer cylinder chamber (60), and the inner side is formed in the inner blade part (45b) defining the inner cylinder chamber (65). Yes. The length of the blade groove (202) is longer than that of the blade (45).

  Thereby, the blade (45) is free to move in the X-axis direction in which the longitudinal direction of the blade (45) is the radial direction of the cylinder (35) with respect to the cylinder (35), and the blade (45) is in the thickness direction. Is movable in the Y direction (more specifically, the direction along the straight portion (201)) perpendicular to the X-axis direction with respect to the piston (40).

  In the configuration described above, when the piston (40) connected to the drive shaft (25) rotates in an eccentric state with respect to the cylinder (35), the piston (40) is formed by the pin (101) and the guide hole (102). Is prevented from rotating. Therefore, as shown in FIG. 9, the annular piston body (43) of the piston (40) slides the blade (45) in the blade groove (202) in the X-axis direction of the cylinder (35), and The linear portion (201) is eccentrically rotated while sliding in the Y-axis direction within the concave portion (45c) of the blade (45). That is, the annular piston body (43) revolves with respect to the cylinder (35).

  Thus, the annular piston body (43) slides in the radial direction of the cylinder (35) together with the blade (45), and the linear portion (201) slides in the recess (45c) of the blade (45). By sliding in a direction perpendicular to the radial direction with respect to the cylinder (35), the contact points between the annular piston main body (43) and the cylinder (35) are sequentially changed from (A) to (H) in FIG. The refrigerant is compressed, and the refrigerant is compressed in the cylinder chamber (60, 65). FIG. 9 is a view showing the operating state of the compression mechanism (30) according to the present embodiment, and the annular piston body (43) is shown at 45 ° intervals from (A) to (H) in FIG. It shows a state of moving in the clockwise direction.

-Effect of the embodiment-
As described above, also in this embodiment, the rotation of the piston (40) is prevented by the movement of the pin (101) being guided by the guide hole (102). Therefore, also in the present embodiment, it is possible to obtain the same effect as the compressor (1) of the first embodiment.

  As described above, in a conventional rotary fluid machine that uses an Oldham coupling consisting of a blade, piston, and cylinder as an anti-rotation mechanism, the blade thickness (the width in the direction in which the piston slides on the blade) is secured above a certain level. There is a need to. As a result, the mass of the blade increases, and vibration based on the inertial force of the blade may increase.

  However, in the present embodiment, the pin (101) and the guide hole (102) prevent the rotation of the piston (40), so that the torque due to the rotation of the piston (40) does not act on the blade (45). Therefore, in this embodiment, stable sliding and durability can be ensured even with a small blade (45) compared to a rotary fluid machine using an Oldham coupling consisting of a blade, a piston, and a cylinder as an anti-rotation mechanism. It becomes possible. In other words, in the present embodiment, the size reduction of the blade (45) makes it possible to reduce the vibration caused by the reciprocating motion (blade inertia force) of the blade (45) during high-speed operation. Furthermore, in this embodiment, since it is not necessary to make the linear part (201) of a piston (40) large, the autorotation torque which acts on a piston (40) does not become large. Therefore, the load acting on each pin (101) is small, and the sliding loss due to the pin (101) is also small. Furthermore, since it is not necessary to increase the thickness of the annular piston main body (43), the piston (40) can be downsized.

<< Embodiment 3 of the Invention >>
Further, the cylinder (35), the piston (40), and the blade (45) may be configured as shown in FIG.

  In this embodiment, as shown in FIG. 10, the cylinder (35) has a cylinder chamber formed in a substantially C-shaped groove shape, and an outer discharge port (54) and an inner discharge port ( 55). A block-like blade (45) that slides inside the C-shaped groove is disposed on the discharge port side of the C-shaped groove.

  Further, the annular piston main body (43) is formed in a substantially C-shaped shape in which a part of the annular ring is divided. One of the divided portions of the annular piston main body (43) comes into contact with the blade (45).

  Further, a pressurizing part (301) into which a gas of a predetermined pressure (for example, a refrigerant gas) is introduced is provided on the outer side of the blade (45) (on the side opposite to the surface in contact with the annular piston main body part (43)). ing. Thus, the blade (45) is pressed against the end of the annular piston main body (43) with a predetermined pressure. With this configuration, the cylinder chamber is partitioned into a high pressure chamber and a low pressure chamber.

  Also in this example, the piston (40) is provided with a plurality of pins (101), and the rear head (50) is provided with a guide hole (102). Therefore, also in this embodiment, the rotation prevention mechanism (100) composed of the pin (101) and the guide hole (102) prevents the rotation of the piston (40), and the piston (40) is prevented from moving relative to the cylinder (35). Revolve.

<Modification>
In each of the above embodiments (any of Embodiments 1 to 3), a sleeve (102a) may be provided inside the guide hole (102) as shown in FIG. In this case, the inner diameter D of the sleeve (102a) is set to D = d + 2e + δ. Where e is the amount of crank eccentricity (that is, the amount of eccentricity of the eccentric portion (27) relative to the main shaft portion (26)), and δ is a minute gap set between the pin (101) and the guide hole (102). It is.

  The sleeve (102a) is made of a material harder than the member (in the above embodiment, the rear head (50)) provided with the guide hole (102). Generally, the sleeve (102a) may be made of bearing steel SUJ or carbon steel obtained by nitriding, carburizing and quenching, or DLC coating.

  For example, if the sleeve (102a) is not provided, the guide hole (102) may be partially worn by partial repeated sliding with the pin (101). However, with such a configuration, it is possible to improve wear resistance (durability).

<< Other Embodiments >>
The above embodiment may be configured as follows.

  For example, in each of the embodiments described above, the compressor (1) has been described. However, the present invention introduces a gas such as a high-pressure refrigerant into the cylinder chamber, and generates the driving force of the rotating shaft when the gas expands. It can be applied to an expander or a pump.

  In the above embodiment, the electric motor (20) is housed in the casing (10). However, the present invention is not limited thereto, and the compression mechanism (30) is driven from the outside of the casing (10). May be.

  The member for providing the pin (101) and the member for forming the guide hole 102 may be reversed. That is, the pin (101) may be provided on the rear head (50) side, and the guide hole (102) may be provided on the piston (40) side. Also in this case, the seal ring groove (103) is preferably provided in the member provided with the guide hole (102).

  Further, the number of pins (101) and the number of guide holes (102) are merely examples, and are not limited to the above examples.

  Further, the piston (40) may be configured as a fixed side cooperative member, the cylinder (35) may be configured as a movable side cooperative member, and the cylinder (35) may revolve with respect to the piston (40). In this case, each pin (101) is provided on either the cylinder side end plate (36) of the cylinder (35) or the support member of the cylinder (35), and the other is provided with a guide hole (102). .

  The rotary fluid machine according to the present invention is useful as a rotary fluid machine in which an annular piston is disposed in an annular space formed in a cylinder, and the cylinder and the annular piston relatively rotate eccentrically. .

It is a longitudinal cross-sectional view of the compressor (rotary fluid machine) which concerns on Embodiment 1 of this invention. It is a cross-sectional view which shows the compression mechanism which concerns on Embodiment 1 of this invention. It is a figure which shows arrangement | positioning of a pin, a guide hole, and a seal ring groove | channel. It is a cross-sectional view which shows operation | movement of the compression mechanism which concerns on Embodiment 1 of this invention. It is a cross-sectional view showing a compression mechanism according to Embodiment 2 of the present invention. The piston which concerns on Embodiment 2 of this invention is shown, (a) is a perspective view, (b) is a top view. The cylinder which concerns on Embodiment 2 of this invention is shown, (a) is a perspective view, (b) is a top view. It is a perspective view which shows the braid | blade which concerns on Embodiment 2 of this invention. It is a cross-sectional view which shows operation | movement of the compression mechanism which concerns on Embodiment 2 of this invention. It is a cross-sectional view which shows the compression mechanism which concerns on Embodiment 3 of this invention. It is a figure which shows the other structural example of a guide hole.

Explanation of symbols

35 Cylinder 36 Cylinder side end plate 40 Piston 41 Piston side end plate 45 Blade 60 Outer cylinder chamber 65 Inner cylinder chamber 70 Seal ring 100 Anti-rotation mechanism 101 Pin 102 Guide hole 103 Seal ring groove

Claims (7)

A cylinder (35) having an annular cylinder chamber (60, 65) and having an end plate (36) on the back surface; and being eccentric to the cylinder (35) and housed in the cylinder chamber (60, 65); The cylinder chamber (60, 65) is divided into an outer working chamber (60) and an inner working chamber (65), and an annular piston (40) having an end plate (41) on the back surface, and each of the working chambers (60, 65). ) Is divided into a high pressure side (61,66) and a low pressure side (62,67), and either one of the piston (40) and the cylinder (35) is a fixed side working member ( 35), the other is a movable side cooperating member (40), and the movable side cooperating member (40) rotates eccentrically with respect to the fixed side cooperating member (35). And
A support member (50) for supporting the movable side cooperating member (40) on the back side of the end plate (41) of the movable side cooperating member (40);
A plurality of pins (101) provided on one of the opposing members of the end plate (41) of the movable side cooperating member (40) and the support member (50), and each of the pins provided on the other opposing member An anti-rotation mechanism (100) that includes a plurality of guide holes (102) into which the pin (101) is inserted and guides the movement of the pin (101) to restrict the rotation of the movable side cooperating member (40); ,
A rotary fluid machine comprising: A cylinder (35) having a cylinder chamber (61, 66, 67) with a C-shaped groove and having an end plate (36) on the back surface, and the cylinder chamber (61, 66) eccentric to the cylinder (35) , 67) and a piston (40) having an end plate (41) on the back, and abutting against one end of the piston (40) in the cylinder chamber (61, 66, 67), the cylinder chamber ( 61, 66, 67) is provided with a blade (45) that divides the outer working chamber (61) and the inner working chamber (67), and either one of the piston (40) and the cylinder (35) is on the fixed side. Rotating fluid configured as a working member (35) and the other as a movable side cooperating member (40) in which the movable side cooperating member (40) rotates eccentrically with respect to the fixed side cooperating member (35) A machine,
A support member (50) for supporting the movable side cooperating member (40) on the back side of the end plate (41) of the movable side cooperating member (40);
A plurality of pins (101) provided on one of the opposing members of the end plate (41) of the movable side cooperating member (40) and the support member (50), and each of the pins provided on the other opposing member An anti-rotation mechanism (100) that includes a plurality of guide holes (102) into which the pin (101) is inserted and guides the movement of the pin (101) to restrict the rotation of the movable side cooperating member (40); ,
A rotary fluid machine comprising: In any one of Claim 1 and Claim 2,
A seal ring (70) for forming a back pressure space for pressing the movable side cooperating member (40) against the fixed side cooperating member (35) is provided between the opposing members.
A rotary fluid machine, wherein a seal ring groove (103) for fitting the seal ring (70) is formed in the opposing member on the guide hole (102) side. In any one of Claim 1 and Claim 2,
A rotary fluid machine, wherein a sleeve harder than the opposing member on the guide hole (102) side is fitted in the guide hole (102). In claim 1,
The blade (45) is formed in a plate shape, and the blade (45) is configured such that the longitudinal direction of the blade (45) can freely move in the X-axis direction that is the radial direction of the cylinder (35) with respect to the cylinder (35). A rotary fluid machine characterized in that the thickness direction of (45) is configured to be movable in the Y direction perpendicular to the X-axis direction with respect to the piston (40). In any one of Claim 1 and Claim 2,
The rotary fluid machine characterized in that the cylinder (35) is configured as a fixed side cooperating member (35) and the piston (40) is configured as a movable side cooperating member (40). In any one of Claim 1 and Claim 2,
The rotary fluid machine, wherein the piston (40) is configured as a fixed side cooperative member (35), and the cylinder (35) is configured as a movable side cooperative member (40).

Images